Forward folding tillage implement

ABSTRACT

A forwardly folding tillage implement carries a number of ground engaging tools on a tool gang frame disposed to the rear of a carrier frame. A rockshaft is disposed between the carrier frame and the tool gang frame and is movable between four rotated positions about two axes of rotation. A control mechanism controls the relative angular position of the rockshaft. A support mechanism is disposed rearwardly of the axes of rotation to support the rear of the tool gang frame above the ground in the field working position. An abutment member restrains the relative rotation between the rockshaft and the tool gang frame to fully support the tool gang frame on the rockshaft upon rotation of the rockshaft.

BACKGROUND OF THE INVENTION

Modern farmers strive to improve the management of increasing amounts offarm acres improving management requires farmers to be able to, quicklyprepare the soil for each season's farming operations. This haste hasdriven the need for more efficient and larger farming equipment.

Implements such as harrows, packers, or combined harrow-packers weresome of the earliest implements to be made with widths exceeding sixtyfeet in the field operating position. As tractor horsepower hasincreased over time, larger tillage implements have been made available.These larger implements require a mechanism for compactly folding theimplement for practical and safe transport over the highway. U.S. Pat.No. 4,821,809, patented by Summach et al., discloses a convenientmechanism for such folding.

The conventional method of folding tillage implements is by folding wingsections along forward aligned axes such that the wings are folded to agenerally upright position. Double folding wing sections may have outersections that fold inwardly and downwardly from the ends of inner wingsections in five section winged implements. In the case of theseconventional wing implements, the minimum implement width that can beachieved by such folding is limited by the width of the center section.As a result, road transport may still be somewhat restricted as theseimplements often exceed twenty feet or more in transport width.

Road transport standards in North America are beginning to follow thestandards set in Europe in which maximum road transport widths andheights for agricultural implements are being defined. Large implementsthat have conventional folding wing sections are not able to be foldedsuch that they fall within width and height limits that may be generally3 meters wide and 4 meters high. Some U.S. states have adopted transportwidth limits of 13.5 ft.

Forward or rear folding implements provide some relief with respect tosuch transport limits. However, implements must also be made to functionwith the accurate seeding ability that conventionally folded implementshave become capable of. Although some rear or forward folding multibartillage implements have been developed, they do not demonstrate theaccurate depth control required for farming operations.

One problem is that a tillage-packer combination for drill seedingrequires the gang supporting tillage elements to be maintained parallelto the ground through a range of adjustable operating levels. Thedrawbar disclosed in Summach '809 raises or lowers the first attachedgang of elements in a rotatable manner through its field and transportranges of motion. A level manner of height adjustment is required fortillage elements.

Another problem that must be overcome for compact folding is theavoidance of the packer elements of the second gang striking the tillageelements of the first gang when raised to the transport position. Ifcompact folding is not required, then the downward rotation of thesuspended second gang may be limited so as not to impact the elements ofthe first gang. But when compact folding is desired, the elements of thesecond gang are in direct alignment with the ground elements of thefirst gang so that alignment is achieved.

Therefore, a multibar implement is required for the tillage of high acrefarms with both speed and efficiency.

SUMMARY OF THE INVENTION

It is an object of the invention to provide a compact folding multibarimplement capable of accurate depth control in field working positions.

It is another object of the invention to provide a compact foldingimplement capable of being configured either as a multibar implement oras a single bar implement for row crop applications, thereby providingeconomy in manufacturing.

It is still another object of this invention to provide a compactfolding implement capable of accurate seeding across its working widtheven while traversing uneven slopes.

An implement having a toolbar or frame to which a first tool gang isattached may also have a second tool gang attached to the rearward endof the first tool gang so both sets of gangs are drawn by the implementframe or toolbar for field operation. Such an implement avails itselffor compact folding in which the first tool gang may be rotated to ageneral upright position and the second tool gang becomes suspended fromthe now upper end of the first gang. Such an implement is patented inU.S. Pat. No. 4,821,809 to Summach et al. According to the patent, theimplement frame or toolbar may be folded for compact folded transport.This design works particularly well for harrow-packer combinedimplements.

One key advantage of this style of folding is that for a harrow-packercombined implement, the packers are pulled inward toward the implementframe substantially before they are lifted from the ground, whichsignificantly reduces the torsion required of the toolbar or frameelements in order to produce sufficient lifting force to effect compactfolding.

This invention provides an offset for the alignment of the second gangelements from the first gang ground elements so they do not impact whenthe implement is folded.

A spiral guide is provided on the pivotal connection on which the secondimplement gang is attached to the first implement gang. When theimplement is folded to transport position, the spiral guide shifts thesecond gang out of alignment with the first gang so their elements donot impact.

These and other objects, features, and advantages are accomplishedaccording to the present invention by providing a forwardly foldingtillage implement that carries a number of ground engaging tools on atool gang frame disposed to the rear of a carrier frame. A rockshaft isdisposed between the carrier frame and the tool gang frame and ismovable between four rotated positions about two axes of rotation. Acontrol mechanism controls the relative angular position of therockshaft. A support mechanism disposed rearwardly of the axes ofrotation to support the rear of the tool gang frame above the ground inthe field working position. An abutment member restrains the relativerotation between the rockshaft and the tool gang frame to fully supportthe tool gang frame on the rockshaft upon rotation of the rockshaft.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic side elevational view of the preferred embodimentof the farm implement in a first position.

FIG. 2 is a schematic side elevational view of the preferred embodimentof the farm implement in a second position.

FIG. 3 is a schematic side elevational view of the preferred embodimentof the farm implement in a third position.

FIG. 4 is a schematic side elevational view of the preferred embodimentof the farm implement in a fourth position.

FIG. 5 is a schematic plan view of the preferred embodiment of the farmimplement in its fully extended working position.

FIG. 5a is a schematic plan view of the preferred embodiment of the farmimplement with its two wings partially folded forward.

FIG. 5b is a schematic plan view of the preferred embodiment of the farmimplement with its two wings fully folded forward.

FIG. 6 is a schematic side elevational view of the preferred embodimentof the farm implement.

FIG. 7 is a schematic side elevational view of the preferred embodimentshown in FIG. 1 showing the depth control in more detail.

FIG. 8 corresponds to FIG. 2 and shows the depth control in the secondrockshaft position.

FIG. 9 is a schematic side elevational view depicting a rockshaftposition intermediate the second and third rockshaft positions.

FIG. 10 is a schematic partial plan view of the tool gang frame of thepreferred embodiment in the position corresponding to FIG. 1.

FIG. 11 is an enlarged schematic detail plan view of the spiral guide ofthe preferred embodiment in the position shown in FIG. 10.

FIG. 12 is an enlarged schematic detail elevational view of the spiralguide of FIGS. 10 and 11.

FIG. 13 is a schematic partial plan view of tool gang frame depictingthe spiral guide of FIG. 10 in the third and fourth rockshaft positions.

FIG. 14 is an enlarged schematic detail plan view of the spiral guidedepicted in FIG. 13.

FIG. 15 is a schematic side elevational view of the tool gang framedepicted in FIGS. 13 and 14 including typical tool 5 raised to atransport position.

FIG. 16 is an enlarged schematic detail elevational view of thepreferred embodiment corresponding to FIG. 1 to show a spring pressuretransfer of weight.

FIG. 17 is similar to FIG. 2 and shows the spring pressure mechanism outof contact with the rockshaft.

FIG. 18 is a schematic plan view of the tool gang frame showing theautomatic locking devices of the preferred embodiment.

FIG. 18a is an enlarged schematic detail plan view of a first joint inthe autolock mechanism positioned on the carrier frame as identified bythe arrow referring to FIG. 18.

FIG. 18b is an enlarged schematic detail plan view of a second joint inthe autolock mechanism positioned on the carrier frame as identified bythe arrow referred to in FIG. 18.

FIG. 19 is a partial schematic plan view of the central portion of thecarrier frame depicting the autolock mechanism in a field operatingposition.

FIG. 19a is a partial schematic elevational view of the central portionof the carrier frame as an orthogonal projection of FIG. 19.

FIG. 19b is an enlarged schematic detail elevational view of a portionof the autolock mechanism positioned on the carrier frame as identifiedby the arrow referring to FIG. 19a.

FIG. 20 is a schematic plan view of the tool gang frame foldedforwardly.

FIG. 20a is an enlarged schematic detail plan view of the first jointsin the autolock mechanism similar to that of FIG. 18a positioned on thecarrier frame as identified by the arrow referring to FIG. 20, butdepicting the mechanism when locked in the transport position.

FIG. 20b is an orthogonal projection of the locked first joints of FIG.20a depicting an elevational view thereof.

FIG. 20c is an enlarged schematic detail plan view of the second jointsimilar to that of FIG. 18b, but depicted in the locked transportposition, as identified by the arrow referring to FIG. 20.

FIGS. 21 and 22 show the implement in the position shown in FIG. 3including more detail of the caster wheel lock in the elevational viewof FIG. 21 and in the rear elevational view of FIG. 22.

FIG. 23 shows the implement in the position depicted in FIG. 4 with thewheels fully castered into the transportation position.

FIG. 23a is a schematic enlarged detail view of the castor wheel lockshown in FIG. 23.

FIG. 23b is a schematic side elevational view of FIGS. 23 and 23a.

FIG. 24 is a schematic side elevational view similar to FIG. 1 butadditionally showing the angled wing axis.

FIG. 24a shows diagrammatically the angled wing axis angle ofinclination.

FIGS. 24b and 24 c show a partial schematic plan view and a partialelevation of the joint between the inner and outer wings in the fieldworking position.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

The preferred embodiment of the farm implement of the invention, asshown in FIG. 1, comprises an implement carrier frame 1 on which ispivotally attached a rockshaft 2 at first pivot 5. Wheels shown at bsupport the carrier frame above the ground. A tool gang frame 3 is alsoattached to the rockshaft 2 at second pivots 6. A ground engaging reardepth control arm 4 is attached to the rear of the tool gang 3 at pivots7. FIG. 1 shows a side elevation of the implement in its lowermost orfirst position. Tool gang frame 3 is disposed parallel to the ground aand is freely rotatable about and supported front and back by first andsecond pivot axes 6 and 7 respectively.

A plurality of ground working tools may be mounted on the tool gangframe for working at variable depths generally parallel to the surfaceof the ground a. A rockshaft 2 is mounted to carrier frame 1 forrotation about pivot axis 5. The angular position of the rockshaft 2 iscontrolled by a hydraulic cylinder d shown fully retracted with therockshaft 2 generally horizontal in FIG. 1. A flange 3 on tool gangframe 3 extends downward and provides pivotal support for tool gangframe 3 about axis 6. A tool support arm 4 is pivotally attached atpivot axis 7 to support tool gang frame 3 at the rear and may carry anadditional soil working tool c.

FIG. 2 shows a side elevation of the implement upon partial extension ofthe hydraulic cylinder d to a second position at which rotation of thetool gang frame 3 about pivot axis 6 ceases when abutment f contactstool gang frame 3 at abutment point g. In the configuration shown inFIG. 1, the rear of tool gang frame 3 is supported by the control arm 4.At the second position shown in FIG. 2, the working tools may beelevated above the ground.

FIG. 3 shows a side elevation of the implement upon further extension ofcylinder d to move the rockshaft to a third position. Between the secondposition shown in FIG. 2 and the third position shown in FIG. 3,rotation of the tool gang frame 3 about second pivot axis 6 isrestrained. Additionally, frame 3 rotates in conjunction with rockshaft2 about first pivot axis 5, is supported on rockshaft 2, and is free ofthe ground. At the third position as shown in FIG. 3, tool gang frameroller j contacts curved track I mounted on carrier frame 1.

As shown in FIG. 4, further extension of cylinder d rotates rockshaft 2about the first axis 5 to a fourth position. Between the third positionand the fourth position, the roller j interacts with curved track i tocontinue rotation of the tool gang frame 3 about the second axis 6 andmoves the abutment f out of contact with the abutment point g.

Referring now to FIG. 5, the carrier frame 1 is preferably arranged as apair of wings symmetrical about the implement center line 308 for travelin direction A. Each of the 2 wings is pivotally attached to the centraltelescoping hitch 301 for motion about a vertical axis at 305. Thecarrier frame 1 is supported on transversely spaced pairs of wheels b.The rockshaft 2 shown in FIGS. 1-4 is not shown on FIGS. 5-6 forsimplicity. A plurality of tool gang frames 3 and support arms 4 areshown. Support tools c are represented schematically. Draft arms 303connect each wing section as at pivotal attachment 304 on frame 1 totelescoping hitch 301 at pivot point 302.

As can be seen in FIGS. 5, 5 a, 5 b, and 6, the carrier frame 1 isfolded forward symmetrically by extension of telescoping hitch 301. Thehitch 301 is extended in length in each successive figure. A pair ofsecondary draft or hitch members 309 is pivotally attached to hitch 301at 302 and extends rearwardly towards secondary hitching point 307.Mounted between members 309 and hitch point 307 are rear hitch members313 which are pivotally connected between pivot points 312 and 314 forrotation about vertical axes. Pivot points 312 are also connected tosupport arms 310 extending from each hitch member to a respective framesection for pivotal movement as at 311.

As can be seen in FIG. 5, a secondary hitch is provided to which anotherimplement may be attached as at 307 for operation in the direction oftravel A. The draft load of the second implement is supported on hitchmembers 309 and 313 along with support arms 310 which act to maintainhitch members 309 and 313 separated from the implement center line 308.

As telescoping hitch 301 is extended and the wings are folded forward asshown in FIG. 5a, the distance B between pivots 305 and hitch point 307is substantially shortened. As telescoping hitch 301 is further extendedand the wings folded to the direction of travel A, the distance B isminimized, thereby bringing the second implement in close proximity tocarrier frame 1 for stability in transport.

In FIG. 6, a schematic elevation of the preferred embodiment is shown inwhich the secondary hitch members 309, 310 and 313 are above carrierframe 1.

Referring now to FIGS. 7 through 9, the preferred embodiment will bedescribed in relation to depth adjustment. FIGS. 7 and 8 correspondgenerally to FIGS. 1 and 2, respectively. FIG. 9 is a side elevationintermediate the second and third rockshaft positions. At another point13 on the rockshaft, offset from the tool gang pivot 6, a depth controllink 12 is pivotally attached. The depth control link is attached at end14 to a first end of a depth control lever 8. The lever is pivotallyattached to the rear part of the tool gang frame 3 at an intermediatepoint between its ends. A roller 10 is attached to the lever's secondend.

The implement depth control 4 consists of an arm 21 which is pivotallyattached at one end 7 to a rear part of the tool gang frame 3 and hasground engaging wheels 23 pivotally attached at its other end having agenerally transverse axis 20. In the field position, roller 10 is incontact with the upper surface 22 of the support arm 21 and the supportarm thereby supports the rearward part of the tool gang frame. This inpart controls the depth of the tool gang frame as the ground wheelsfollow the surface of the ground.

In field positions, the tool gang frame 3 may pivot on attachment pivot6 as ground wheels 23 and ground wheels 24 follow the slope of theground. The tool gang is supported parallel to the ground between theframe ground wheels and depth gage ground wheels. A screw connects thedepth control link to the depth control lever. The screw may be utilizedto adjust the effective length of the depth control link for levelingthe tool gang frame. Each tool gang frame may thereby be independentlyleveled. Alternatively, a turnbuckle or similar length adjusting meansmay be used in the depth control link.

The rockshaft 2 of respective frame sections is rotated clockwise orcounterclockwise as shown in the view in FIGS. 7 and 8 to respectivelylower or raise the attached tool gang frame sections. The depth controllink 12 is drawn forward relative to the tool gang frame 3 when therockshaft is rotated counterclockwise to raise the tool gang frame. Thedepth control link causes the depth control lever 8 to rotate clockwisein the view of FIG. 8 and the roller on its second end bears down on thedepth control support arm 4, thereby causing rotation of the depthcontrol in a clockwise direction. The attachment points of the linkageon the rockshaft and on the depth control lever are such that the reardepth control is rotated an amount causing an equal rise at the rear ofthe tool gang when the rockshaft raises the front of the tool gang asshown in FIGS. 7 and 8.

The preferred embodiment will now be described in respect of its spiralguide in conjunction with FIGS. 10 through 14. The spiral guide 60 ismade to have an axis generally concentric with the pivot 7 by whichpacker arm 21 is attached to tillage gang frame 3. The packer arm has aspindle 71 extending its pivotally connected end on which a roller 70 issecured. The spiral guide 60 has a non-spiral surface 61 which theroller 70 follows when the implement is in the field position, and whichrestricts the sideways movement of the packer arm on the pivot shaft 7,as shown in FIGS. 10-15. As the implement is folded to the transportposition as shown in FIGS. 10-15, the roller 70 leaves the non-spiralsurface 61 and follows the angled or spiral surface 62. The roller 70 islimited by opposing spiral surface 63. As the packer pivots downwardlyfrom the end of the tool gang frame 3 or tillage gang, the roller iscaught in a track formed between the spiral surfaces 62,63. The spiralshape is such that the controlled movement causes a sideways or lateraloffset 69 of the packer elements as the packer is suspended and rotatesdownwardly when being raised to the transport position. The spiralsurfaces 62,63 control the roller movement and cause the packer toreturn to alignment with the tillage elements when lowered into thefield position.

Referring now to FIGS. 16 and 17, it is shown that the preferredembodiment may include a spring pressure mechanism to transfer weight tothe tool gang frame 3. In FIGS. 16 and 17, the spring 50 may bepre-compressed by selectively shortening the available stroke of rod 51,such as by a nut and tread on rod 50. This provides of a large unsprungrange of rotation between the first and second positions while providingthe operator with additional adjustments.

In particular, as shown in FIG. 16, the tool gang frame 3 is depicted inits first position, the lowermost position, as viewed in FIG. 1. Spring50 acts between frame 3 and rod 51 to advantageously transfer weight tothe frame. The spring is adjustable by lengthening or shortening the rod53. Arm 52 acts between rod 51 and rockshaft 2 and is pivotally attachedto provide for abutment of rod 53, as at 54 in FIG. 16. In the secondrockshaft position, the highest field position, rod 53 loses abuttingcontact as at 54 in FIG. 17 and rod 51 is fully retracted by spring 50.

As shown in FIGS. 18-20c, automatic locking is provided by means oflevers connected between the frame position control cylinders shown inFIG. 19. The control cylinders have a limited degree of freedom ofmovement between the lever and the frame and the cylinders actuatingmovement. Interconnection of the lever with locks provides for automaticoperation of the locks at the two extents of the cylinders' extension asshown so as to not interfere with extension and contraction of thecylinders and corresponding frame movement.

Referring now to FIGS. 18 and 20, the implement is shown with innerwings w1 and outer wings w2 symmetrically joined along the implementcenter line for pivotal relative motion between wings w1 and w2 about anaxis generally in the direction of travel when in the field workingposition.

FIG. 21 shows the implement in the position shown in FIG. 3, and FIG. 22shows wheels b as item 24 for castering about a vertical axis at 25 withextending arm 26 in the field working position. Item f is referred to as15 in FIGS. 21-23b.

FIG. 23, and in more detail in FIG. 23a, the transport condition withwheels 24 fully castered about axis 25 and arm 26 locked in position byplate 27 is shown. FIG. 23b shows the arm 26 in recess in plate 27.

FIG. 24 shows the implement in the position of FIG. 1. Outer wingsection w2 is pivotally joined to inner wing section w1 at forward andrearward points 51 and 52 respectively. In FIG. 24a, angled wing axis 53is depicted as inclined downward and forward in the direction of travelA by amount Dd. FIG. 24b shows a partial plan view of inner wing sectionw1 and outer wing section w2 along with forward and rearward members w1a and w1 b of inner wing w1. FIG. 24c shows a partial rear elevation ofFIG. 24b.

What is claimed is:
 1. A forward folding tillage implement comprising: ahitch member adapted at a forward end for connection to a prime mover;left and right wing members pivotally connected to said hitch member,each said wing member being pivotally movable about a generally verticalpivot axis carried by said hitch member between a transversely extendingoperating position and a longitudinally extending transport position,said hitch member including a latch mechanism cooperable with said innerwing sections to retain said wing members in said transport position;each said wing member including an inner wing section pivotallyconnected to the corresponding said pivot axis and an outer wing sectionpivotally connected to said corresponding inner wing section formovement relative thereto about an oscillation axis, said oscillationaxis extending generally longitudinally when said wing members are insaid operating position to permit said outer wing sections to movegenerally vertically relative to the corresponding said inner wingsections when in said operating position thus allowing said wing membersto follow ground undulations, each said oscillation axis being inclineddownwardly and forwardly when said wing members are in said operatingposition; and ground engaging wheels supporting each said inner andouter wing section, said ground engaging wheels being movable relativeto the corresponding wing section to permit a re-orientation relativethereto between said operating and said transport positions.
 2. Theimplement of claim 1, wherein a hydraulic cylinder interconnects saidhitch member and each of said inner wing sections to effect pivotalmovement of said wing members between said operating and said transportpositions.
 3. The implement of claim 2, wherein one of said hydrauliccylinders is connected to an actuation bracket pivotally supported onone of said inner wing sections for movement between first and secondpositions, said actuation bracket being connected to said latchmechanism to effect operation thereof.
 4. The implement of claim 3,wherein said latch mechanism comprises: a hook member carried by each ofsaid inner wing sections; a pivoted member associated with one of saidhook members and being pivotally movable between a latching position andan unlatching position; an actuation link interconnecting said actuationbracket and said pivoted member to effect movement of said pivotedmember in response to said pivotal movement of said actuation bracket;and a latch keeper supported on said hitch member for engagement withsaid hook members when said wing member move into said transportposition, said latch keeper being movable between an engaging positionand a disengaging position.
 5. The implement of claim 4, wherein themovement of said one of said hydraulic cylinders to effect pivotalmovement of said corresponding wing member from said transport positioncauses said pivotal movement of said actuation bracket from said firstposition to said second position, which in turn effects the pivotalmovement of said pivoted member from said latching position to saidunlatching position to force said latch keeper into said disengagingposition, whereby said corresponding hook member is released to permitsaid corresponding wing member to move into said operating position. 6.The implement of claim 4, wherein a wing lock mechanism is connected tosaid actuation bracket for movement in concert therewith such that saidlock mechanism is engagable with the opposing said wing member when saidactuation bracket is in said second position, said lock mechanism beingoperable to fix the opposing said wing member in said operatingposition.
 7. The implement of claim 6, wherein the movement of saidactuation bracket from said second position to said first positioncauses said lock member to release said opposing wing member, thuspermitting pivotal movement thereof into said transport position.
 8. Aforward folding tillage implement comprising: a hitch member adapted ata forward end for connection to a prime mover; left and right wingmembers pivotally connected to said hitch member, each said wing memberbeing pivotally movable about a generally vertical pivot axis carried bysaid hitch member between a transversely extending operating positionand a longitudinally extending transport position; a hydraulic cylinderinterconnects said hitch member and each of said wing members to effectpivotal movement of said wing members between said operating and saidtransport positions; an actuation bracket pivotally supported on one ofsaid wing members for movement between first and second positions, saidactuation bracket being connected to one of said hydraulic cylinders toeffect movement thereof; a latch mechanism for retaining said wingmembers in said transport position, said latch mechanism beingoperatively associated with said actuation bracket to effect movementthereof between a latching configuration in which said wing members areretained in said transport position and an unlatching configuration inwhich said wing members are free to move into said operating position.9. The implement of claim 8, wherein said latch mechanism comprises: ahook member carried by each of said wing members; a pivoted memberassociated with one of said hook members and being pivotally movablebetween a latching position and an unlatching position; an actuationlink interconnecting said actuation bracket and said pivoted member toeffect movement of said pivoted member in response to said pivotalmovement of said actuation bracket; and a latch keeper supported on saidhitch member for engagement with said hook members when said wing membermove into said transport position, said latch keeper being movablebetween an engaging position and a disengaging position.
 10. Theimplement of claim 9, wherein the movement of said one of said hydrauliccylinders to effect pivotal movement of said corresponding wing memberfrom said transport position causes said pivotal movement of saidactuation bracket from said first position to said second position,which in turn effects the pivotal movement of said pivoted member fromsaid latching position to said unlatching position to force said latchkeeper into said disengaging position, whereby said corresponding hookmember is released to permit said corresponding wing member to move intosaid operating position.
 11. The implement of claim 10, wherein a winglock mechanism is connected to said actuation bracket for movement inconcert therewith such that said lock mechanism is engagable with theopposing said wing member when said actuation bracket is in said secondposition, said lock mechanism being operable to fix the opposing saidwing member in said operating position.
 12. The implement of claim 11,wherein the movement of said actuation bracket from said second positionto said first position causes said lock member to release said opposingwing member, thus permitting pivotal movement thereof into saidtransport position.
 13. A forward folding tillage implement comprising:a hitch member adapted at a forward end for connection to a prime mover;left and right wing members pivotally connected to said hitch member,each said wing member being pivotally movable about a generally verticalpivot axis carried by said hitch member between a transversely extendingoperating position and a longitudinally extending transport position;and each said wing member including an inner wing section pivotallyconnected to the corresponding said pivot axis and an outer wing sectionpivotally connected to said corresponding inner wing section formovement relative thereto about an oscillation axis, each saidoscillation axis extending generally longitudinally, downwardly andforwardly when said wing members are in said operating position topermit said outer wing sections to move generally vertically relative tothe corresponding said inner wing sections when in said operatingposition thus allowing said wing members to follow ground undulations.14. The implement of claim 13, wherein said hitch member includes alatch mechanism to retain said wing members in said transport position,said latch mechanism being cooperable with said inner wing sections toretain said wing members in said transport position.
 15. The implementof claim 14, wherein each said inner and outer wing section aresupported by corresponding ground engaging wheels that are movablerelative to the corresponding wing section to permit re-orientationrelative thereto between said operating and said transport positions.